AT413140B - Gear pump - Google Patents

Gear pump Download PDF

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Publication number
AT413140B
AT413140B AT0049303A AT4932003A AT413140B AT 413140 B AT413140 B AT 413140B AT 0049303 A AT0049303 A AT 0049303A AT 4932003 A AT4932003 A AT 4932003A AT 413140 B AT413140 B AT 413140B
Authority
AT
Austria
Prior art keywords
gear
pressure
gear pump
pump
displaceable
Prior art date
Application number
AT0049303A
Other languages
German (de)
Other versions
ATA4932003A (en
Inventor
Alfred Ing Goetschhofer
Original Assignee
Tcg Unitech Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Tcg Unitech Ag filed Critical Tcg Unitech Ag
Priority to AT0049303A priority Critical patent/AT413140B/en
Publication of ATA4932003A publication Critical patent/ATA4932003A/en
Application granted granted Critical
Publication of AT413140B publication Critical patent/AT413140B/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/185Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023Axial sealings for working fluid
    • F04C15/0026Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons

Description


   <Desc / Clms Page number 1>
 



  The invention relates to a variable displacement pump with two externally toothed gears meshing with each other, which are rotatably mounted in a pumping chamber of a pump housing, wherein at least one of the two gears via a drive shaft is driven and one of the two gears, preferably the aborted gear in Direction of the axis of this gear is designed to be displaceable.



  Conventional gear pumps with two intermeshing externally toothed gears have a drive shaft driven gear which drives the second gear. In addition to the tooth profile and the pump speed, the gear engagement width is decisive for the volume flow of the pumped medium through the gear pump.



  Losses caused by the head play of the gears to the pump housing and the play of the gap gauge at the end faces of the gears are reflected in the efficiency of the gear pump. Gear pumps of this type are commonly used for oil pumps of internal combustion engines. Conventional oil pumps are coupled by a rigid, non-variable drive such as chain, gears, timing belt, etc. in a fixed speed ratio with the crankshaft of the engine.

   With increasing speed of the engine, the oil pump speed is increased and thus the capacity of the oil pump in relation to the engine speed. Oil pumps are generally designed for the worst case of oil supply to the engine over the entire speed field, which is the idle speed with the largest gap cross section in the bearings, including all other consumers on the engine such as pistons, spray nozzle for piston cooling or turbocharger, etc. From this design results in that the oil pump delivers at higher engine speeds over a multiple of the required amount of oil for high engine speeds.

   The quantity control of the actual consumption of the respective engine operating state is usually carried out by pressure control and Absteuern the excess amount of oil delivered in the oil sump, or by returning to the intake port of the pump. Since the gears of the pump thus always promote the maximum amount of oil, regardless of the actual needs always approximately the same high drive power must be provided. This has a disadvantageous effect on the efficiency.



  From DE 196 31 956 A1 a gear pump with adjustable displacement volume is known. A gear of the gear pump has openings, which extend from a coaxial bore to the tooth spaces. In the bore is a rotary valve with at least one web which has a part-cylindrical lateral surface and defines an axial recess on the rotary valve, rotatably mounted on a gear carrying a shaft. The web abuts with its lateral surface in the inside of the bore and the recess is connected to the low pressure side of the pump. By adjusting the rotary valve, the displacer volume can be adjusted according to the opening width of the Druchbrüche. The adjustment mechanism is relatively expensive and has many complex shaped items.



  Furthermore, it is known to adjust the delivery volume by changing the tooth engagement width. In this case, at least one of the two gears can be displaced in the axial direction and thus the tooth engagement width can be changed, wherein partially in the tooth gaps engaging patches are necessary to avoid dead space. Such gear pumps are known, for example, from GB 2 265 945 A, AT 003 767 U1, DE 41 21 074 A1 or RU 2 177 085 C. In addition to the relatively large number of complex parts to be produced, it is disadvantageous that in the axial direction, the gear pump takes up relatively much space through the axial gear adjustment to complete. DE 199 24 057 A1 describes a gear machine with two intermeshing gears on the axial sealing on the side surfaces axially displaceable components are pressed.

   The two components are loaded with different large resulting forces in the axial direction and pressed against the gears, which are thereby moved in the axial direction in a defined position. This is to avoid a widened inlet track in the housing.



  The object of the invention is to avoid these disadvantages in the simplest possible way

 <Desc / Clms Page number 2>

 a gear pump of the type mentioned to achieve a control of the delivery volume.



  According to the invention, it is provided that a gap defined by the distance measured in the axial direction between a substantially planar first inner side wall of the delivery chamber of the pump housing and a first end side of the displaceable gearwheel can be changed. Preferably, it is provided that the gap dimension in a range between 0 to d / 5, preferably in a range between 0 to d / 50 is variable, where d is the outer diameter of the displaceable gear.



  In contrast to the known variable gear pumps with axially displaceable gears, the control of the delivery volume is mainly due to the change in the gap and thus the gap losses. Patches for filling the dead spaces, which intervene, for example, in the tooth gaps, are not necessary. Due to the pressure or delivery rate control via the change in the gap size, extremely small axial displacements are sufficient, since the gap size influences the pressure and delivery rate of the gear pump very much.



  In order to enable a lateral deflection of the displaceable gear in a simple manner, it is provided that one of the first inner side wall opposite and parallel to this second inner side wall of the delivery chamber in the region of a first end face remote from the second end face of the sliding gear concentric with the axis, has substantially cylindrical recess whose diameter is greater than the outer diameter of the gear at least in the region of the displaceable gear.



  It is extremely advantageous if in the region of the niche a preferably plate-shaped sealing disc is arranged, which separates the delivery chamber of the pump housing from a dead space within the niche, wherein preferably the sealing disc is non-rotatably connected to the displaceable gear. Due to the preferably plate-shaped sealing disc, a lateral seal is made possible to the dead space. In order to avoid pressure peaks, it is further provided that the sealing disc has at least one radial relief groove on the side facing the second end face in the region of each interdental space of the displaceable toothed wheel.

   It is particularly advantageous if in the region of the pressure-side tooth engagement of the two gears on the side of the sealing disc in the first inner side wall opposite second inner side wall of the delivery chamber an outlet groove is formed, which is arranged so that during each revolution of the sealing disc each relief groove at least once communicates with the exit groove. In particular, in the unregulated initial position of the gears, in which the gears mesh with each other over their entire gear width, pressure spraying can be effectively avoided by the relief grooves and the Quetschölaustrittsnut. At higher speeds and large gap size pressure pulsations can be compensated by the resulting gap space.



  The pressure and flow control is carried out in the described gear pump completely without control piston or valves, whereby a very compact design can be achieved.



  Since the control is performed by changing the gap losses, and adjusts a lower suction / pressure performance in the control range, the gear pump in the control range also has a much lower power consumption. Due to the extremely small displacement of the gears, the teeth are almost always bearing on the entire tooth flank, whereby they are subject to a much lower wear than over the meshing width regulated gear pumps.



  In a very advantageous embodiment of the invention it is provided that the dead space emanates a leakage channel, wherein preferably the leakage channel formed by a preferably spiral shaped in the pump housing adjacent to the control shaft leakage groove

 <Desc / Clms Page 3>

 is. As a result, leakages penetrating into the dead space can be reliably dissipated in the normal operating mode between the sealing disk and the pump housing.



  In order to avoid the occurrence of pressure peaks in the dead space and to ensure a safe pressure relief, it is provided in a preferred embodiment that the dead space via a discharge channel with a pressure sink, preferably with the suction side or the pump environment is strömungsverbindbar, preferably in the discharge channel in a direction the pressure sink opening pressure relief valve is arranged. The pressure relief valve has the task to prevent a pressure increase in the dead space. As a result, a malfunction of the control characteristics of the gear pump can be avoided, which is particularly important in cold run-up and radially sealed sealing disc of importance.



  In an extremely advantageous embodiment, it is provided that the sealing disc has at least one peripheral sealing groove in its jacket region. Due to the circumferential sealing groove can be dispensed with radial relief grooves.



  A simple displacement of the toothed wheel can be achieved if the displaceable toothed wheel, preferably also the sealing disc, is arranged rigidly on a control shaft which is rotatable in the pump housing and displaceable in the direction of the axis. In a particularly preferred embodiment, it is provided that the control shaft for axial adjustment has at least one pressure piston which adjoins a pressure chamber connectable to a pressure medium, wherein preferably the pressure medium is formed by the fluid and the pressure chamber is fluidly connected to the pressure side of the gear pump.



  Alternatively, it can also be provided that the pressure chamber is connected to an external pressure source or a pure oil control device. This allows external control. The provision of the control shaft can be done via a trained example as a compression spring return spring. In an alternative embodiment, it can be provided that the control shaft, at least in one direction, is adjustable by an electric servomotor.



  The invention will be explained in more detail below with reference to FIGS.



  1 shows the gear pump according to the invention in a section along the line II in FIGS. 1 and 2, FIG. 2 shows the gear pump in a section along the line II-II in FIG. 1 in the rest position in a first embodiment according to the invention, Fig. 3 shows this gear pump in a section along the line 11-11 in Fig. 1 in a control position, Fig. 4 and 5, a gear pump in a second embodiment according to the invention analogous to FIGS. 2 and 3 and Fig. 6 is a sealing disc in an alternative Embodiment of the invention in a longitudinal section.



  Functionally identical components are provided in the embodiments with the same reference numerals.



  The gear pump 1 has two meshing, externally toothed gears 2, 3, which are rotatably arranged in a delivery chamber 11a of a pump housing 4. The gear 3 is driven by a drive shaft 5 and drives the gear 2 at. The aborted gear 2 is arranged together with a sealing disc 6 on a control shaft 7 and can be moved with this in the direction of the axis 2 'of the gear 2, as indicated by the arrow P. With reference numeral 8, the suction side, with reference numeral 9, the pressure side of the gear pump 1 and the arrows S, the flow direction of the medium indicated.



  By moving the control shaft 7 and thus of the displaceable gear 2, the apparent in Fig. 3 gap 10 can be changed. The gap 10 is as a distance between a flat first inner side wall 11 a of the pumping chamber 11 of the pump housing 4 and

 <Desc / Clms Page number 4>

 a first end face 2a of the sliding gear 2 defined. With the outer diameter d of the displaceable gear 2, the adjustment range of the gap 10 is between 0 to d / 5, preferably between 0 to d / 50, the rest state shown in Fig. 2 is assigned a minimum constructive value for the gap 10.



  The regulation of the pressure or the flow rate is accomplished via the gap 10 and thus by changing the gap losses. This can be dispensed with filler, in particular for filling the interdental spaces 14. Even a slight displacement of the displaceable gear 2 is sufficient to change the gap 10 to a sufficient extent.



  In order to enable a lateral deflection of the gear 2, the first inner side wall 11a opposite second inner side wall 11b concentric with the axis 2 'has a substantially cylindrical recess 22 whose diameter D in the region of the second end face 2b of the sliding gear 2 is slightly larger than the outer diameter d of the gear 2.



  The arranged in the niche 22 plate or annular sealing disc 6 serves to seal the gear wheels 2.3 receiving the delivery space 11von a necessary for the displacement of the gear 2 dead space 12 within the niche 22. In order to avoid an increase in pressure in the dead space 12, this is connected via a in Figs. 2 and 3 and Fig. 4 and 5 dotted relief channel 25 with a pressure sink, which the suction chamber 8 or the pump environment, such as the oil space of an oil pan, can be. In the discharge channel 25 a opening in the direction of the pressure sink pressure relief valve 26 is arranged. The sealing disk 6 has radial relief grooves 13 arranged on the side of the space between the teeth, on the side of the second end face 2b of the displaceable gearwheel 2 facing away from the first end face 2a.



  Each radial relief groove 13 is arranged in each case in the region of a tooth space 14 of the displaceable gear 2 and communicates during one revolution of the displaceable gear 2 with an outlet groove 15 which is formed in the pressure-side engagement portion 23 of the two gears 2.3 in the pump housing 4. By the relief grooves 13 and the outlet groove 15 pressure peaks, especially at low speed in the unregulated idle state of the gear pump 1 are avoided.



  On radial relief grooves 13 can be largely dispensed with, if the sealing disc 6, as shown in Fig. 6, is provided in its shell region with at least one circumferential sealing groove 27 which acts as a labyrinth seal and compensates pressure peaks.



  With a 4a connected by screws 16 to the pump housing 4 pump housing cover is called.



  The indicated by reference numeral 29 Leckagenut has the task to dissipate into the dead space 12 through the annular gap between the sealing disc 6 and the pump housing 4 incoming leaks to the outside. The leakage groove 29 is designed, for example, helical and connects the dead space 12 with a spring chamber 30. In order to reliably dissipate leaks in normal operation, the sum of the cross-sectional areas of bearing clearance of the control shaft 7 and the leakage groove 29 is at least as large as the annular gap between the sealing disc 6 and pump housing 4.



  The control shaft 7 has a pressure piston 17, which is sealed to the pump housing cover 4a through the seal 18. The pressure piston 17 is adjacent to a pressure chamber 19 which is closed by the closure screw 20. In the pressure chamber 19 opens a Drucköleintritt 21 which is fluidly connected to the pressure side 9 of the gear pump 1 (Fig. 2,3), or which with an external pressure source or a so-called pure oil

 <Desc / Clms Page number 5>

 Control (oil pressure, taken after the oil filter) in communication (Fig. 4.5). Thus, the deflection of the control shaft 7 is effected in the control position by the delivery pressure of the gear pump 1. The return to the rest position via a arranged in the spring chamber 30 return spring 28, for example, a compression spring, or an electric servomotor.

   Optionally, the deflection of the control shaft 7 in the control position instead of by the pump pressure also done by the electric servomotor.



  1. gear pump (1) with variable delivery volume with two toothed engagement (23) stationary externally toothed gears (2,3), which are rotatably mounted in a delivery chamber (11) of a pump housing (4), wherein at least one of the two
Gear wheels (3) via a drive shaft (5) can be driven and one of the two gears (2), preferably the aborted gear (2), in the direction of the axis (2 ') of this gear wheel (2) slidably formed, characterized in that a distance, defined by the distance measured in the axial direction, between a substantially planar first inner side wall (11a) of the delivery chamber (11) of the pump housing (4) and a first end side (2a) of the displaceable gear (2) Gap (10) is variable.

Claims (1)

  1. 2. Gear pump (1) according to claim 1, characterized in that the gap dimension (10) in a range between 0 to d / 5, preferably in a range between 0 to d / 50 is changeable ver, where d is the outer diameter of the displaceable Gear (2) is.
    3. Gear pump (1) according to claim 1 or 2, characterized in that one of the first Inner side wall (11a) opposite and parallel to this parallel second inner side wall (11b) of the conveying space (11) in the region of one of the first end (2a) facing away from the second end face (2b) of the displaceable gear (2) concentric with Has axis (2 ') formed, substantially cylindrical niche (22) whose diameter (D) at least in the region of the displaceable gear (2) greater than the Outside diameter d of the gear (2).
    4. gear pump (1) according to claim 3, characterized in that in the region of the niche (22) a preferably plate-shaped sealing disc (6) is arranged, which the conveying space (11) of the pump housing (4) of a dead space (12). inside the niche (22) separates from the delivery chamber (11), wherein preferably the sealing disc (6) rotatably connected to the displaceable gear (2).
    5. gear pump (1) according to claim 4, characterized in that the sealing disc (6) on the second end face (2b) facing side in the region of each Zahnzwischenrau- mes (14) of the displaceable gear (2) at least one radial relief groove (13 ) having.
    6. gear pump (1) according to claim 5, characterized in that in the region of the pressure-side tooth engagement (23) of the two gears (2,3) on the side of the sealing disc (6) in the first inner side wall (11 a) opposite the second Inner side wall (11b) of the delivery chamber (11) an outlet groove (15) is formed, which is arranged so that during each revolution of the sealing disc (6) each relief groove (13) at least once with the outlet groove (15) communicates.
    7. Gear pump (1) according to one of claims 4 to 6, characterized in that of Dead space (12) runs out of a leakage channel.
    8. gear pump (1) according to claim 7, characterized in that the leakage channel by a preferably spiral in the pump housing (4) adjacent to the Re-  <Desc / Clms Page number 6>  gelwelle (7) formed leaking groove (29) is formed.
    9. gear (1) according to one of claims 4 to 8, characterized in that the Dead space (12) via a discharge channel (25) with a pressure sink, preferably with the Suction side (8) or the pump environment is flow connected, wherein preferably in the discharge channel (25) in the direction of the pressure sink opening pressure relief valve (26) is arranged.
    10. Gear pump (1) according to one of claims 4 to 9, characterized in that the Sealing disc (6) in its jacket region at least one circumferential sealing groove (27) has up.
    11. Gear pump (1) according to one of claims 1 to 10, characterized in that the displaceable gear (2), preferably also the sealing disc (6), rigidly on a in Pump housing (4) is rotatable and in the direction of the axis (2 ') displaceable control shaft (7) is arranged.
    12. gear pump (1) according to claim 11, characterized in that the control shaft (7) for axial adjustment at least one pressure piston (17) which adjoins a connectable to a pressure medium pressure chamber (19).
    13. Gear pump (1) according to claim 12, characterized in that the pressure medium is formed by the conveying medium and the pressure chamber (19) with the pressure side (9) of the Gear pump (1) is fluidly connected.
    14. gear pump (1) according to claim 12, characterized in that the pressure chamber (19) is connected to an external pressure source or a pure oil control device.
    15. gear pump (1) according to one of claims 9 to 14, characterized in that on the control shaft (7) counter to the deflection by the pressure piston (17) acts a restoring spring.
    16. Gear pump (1) according to one of claims 9 to 15, characterized in that the Control shaft (7) is adjustable in at least one direction by an electric servomotor.
AT0049303A 2003-03-28 2003-03-28 Gear pump AT413140B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT0049303A AT413140B (en) 2003-03-28 2003-03-28 Gear pump

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
AT0049303A AT413140B (en) 2003-03-28 2003-03-28 Gear pump
PL04450056T PL1462654T3 (en) 2003-03-28 2004-03-11 Gearpump
EP04450056A EP1462654B1 (en) 2003-03-28 2004-03-11 Gearpump
ES04450056T ES2247580T3 (en) 2003-03-28 2004-03-11 GEAR PUMP.
AT04450056T AT307293T (en) 2003-03-28 2004-03-11 Gear pump
DE502004000102T DE502004000102D1 (en) 2003-03-28 2004-03-11 gear pump
US10/809,907 US7137798B2 (en) 2003-03-28 2004-03-26 Gear pump with variable throughput volume
JP2004094858A JP2004301125A (en) 2003-03-28 2004-03-29 Gear pump

Publications (2)

Publication Number Publication Date
ATA4932003A ATA4932003A (en) 2005-04-15
AT413140B true AT413140B (en) 2005-11-15

Family

ID=32777542

Family Applications (2)

Application Number Title Priority Date Filing Date
AT0049303A AT413140B (en) 2003-03-28 2003-03-28 Gear pump
AT04450056T AT307293T (en) 2003-03-28 2004-03-11 Gear pump

Family Applications After (1)

Application Number Title Priority Date Filing Date
AT04450056T AT307293T (en) 2003-03-28 2004-03-11 Gear pump

Country Status (7)

Country Link
US (1) US7137798B2 (en)
EP (1) EP1462654B1 (en)
JP (1) JP2004301125A (en)
AT (2) AT413140B (en)
DE (1) DE502004000102D1 (en)
ES (1) ES2247580T3 (en)
PL (1) PL1462654T3 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010038430A1 (en) * 2010-07-26 2012-01-26 Schwäbische Hüttenwerke Automotive GmbH Positive displacement pump with suction groove

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070111855A1 (en) * 2003-12-10 2007-05-17 Dieter Voigt Engine speed-dependent pressure regulation of oil pumps
DE102004026048A1 (en) * 2004-05-25 2005-12-29 Cor Pumps + Compressors Ag Gap leakage current control
US8302353B2 (en) 2004-10-15 2012-11-06 Thomas Bren Water intrusion prevention method and apparatus
US7832997B2 (en) * 2004-12-22 2010-11-16 Magna Powertrain, Inc. Variable capacity gerotor pump
US20070201989A1 (en) * 2005-10-14 2007-08-30 Parker-Hannifin Low ripple gear pump/motor
US7717690B2 (en) * 2006-08-15 2010-05-18 Tbk Co., Ltd. Gear pump
BRPI1001768A2 (en) * 2010-05-24 2012-01-24 Jose Luiz Bertazzolli Continuously Variable Transmission
JP5909966B2 (en) * 2011-09-30 2016-04-27 株式会社Lixil Pump and cleaning device
RU2511848C1 (en) * 2012-11-06 2014-04-10 Анатолий Константинович Маришкин Adjustable gear-type pump
CN105041639A (en) * 2015-08-27 2015-11-11 刘凡 External gearing variable gear pump
US10113546B2 (en) 2016-08-16 2018-10-30 Caterpillar Inc. Pump for an engine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4121074A1 (en) * 1991-06-26 1993-01-07 Pierburg Gmbh External gear pump - has main drive gear fixed inside housing and driven gear adjusted by pressure differential piston action
GB2265945A (en) * 1992-04-10 1993-10-13 Charles Lee Variable capacity gear pump.
DE19631956A1 (en) * 1996-08-08 1998-02-12 Danfoss As Gear pump for fluids
AT3767U1 (en) * 1999-05-06 2000-07-25 Avl List Gmbh Gear pump with changeable conveyor volume
DE19924057A1 (en) * 1999-05-26 2000-11-30 Bosch Gmbh Robert Gearwheel machine for hydrostatic drives has two axially displaceable component parts pressing axially onto side faces of gearwheels with different sized forces
RU2177085C2 (en) * 1999-05-07 2001-12-20 Бодогазин Сергей Борисович Variable-capacity gear pump

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2052419A (en) * 1934-09-14 1936-08-25 Manning Maxwell & Moore Inc Variable delivery gear pump
US2434135A (en) * 1942-12-02 1948-01-06 Eaton Mfg Co Gear pump structure
US3110265A (en) * 1961-08-31 1963-11-12 Wendell S Miller Gear type fluid handling device
DE2806951A1 (en) 1978-02-18 1979-08-30 Bayer Ag N-ACYLAMINOHYDROXYNAPHTHALINE SULPHONIC ACID SALTS
PL137198B1 (en) * 1982-07-21 1986-05-31 Typowych Elementow Hydrauliki Hydraulic gear pump or motor
DE3528651A1 (en) * 1985-08-09 1987-02-19 Rohs Hans Guenther Prof Dr Ing GEAR PUMP
CN1009024B (en) * 1986-09-24 1990-08-01 郑悦 Axial deflection pump or motor
US5306127A (en) * 1993-03-08 1994-04-26 Kinney Gerald R Fluid pump with axially adjustable gears
US5724812A (en) * 1996-02-16 1998-03-10 Baker; William E. Variable displacement apparatus and method of using same
US6244839B1 (en) * 1997-11-14 2001-06-12 University Of Arkansas Pressure compensated variable displacement internal gear pumps
JPH11343982A (en) * 1998-05-30 1999-12-14 Suzuki Motor Corp Trochoid oil pump
DE19847132C2 (en) * 1998-10-13 2001-05-31 Schwaebische Huettenwerke Gmbh External gear pump with delivery volume limitation

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4121074A1 (en) * 1991-06-26 1993-01-07 Pierburg Gmbh External gear pump - has main drive gear fixed inside housing and driven gear adjusted by pressure differential piston action
GB2265945A (en) * 1992-04-10 1993-10-13 Charles Lee Variable capacity gear pump.
DE19631956A1 (en) * 1996-08-08 1998-02-12 Danfoss As Gear pump for fluids
AT3767U1 (en) * 1999-05-06 2000-07-25 Avl List Gmbh Gear pump with changeable conveyor volume
RU2177085C2 (en) * 1999-05-07 2001-12-20 Бодогазин Сергей Борисович Variable-capacity gear pump
DE19924057A1 (en) * 1999-05-26 2000-11-30 Bosch Gmbh Robert Gearwheel machine for hydrostatic drives has two axially displaceable component parts pressing axially onto side faces of gearwheels with different sized forces

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010038430A1 (en) * 2010-07-26 2012-01-26 Schwäbische Hüttenwerke Automotive GmbH Positive displacement pump with suction groove
DE102010038430A8 (en) * 2010-07-26 2012-03-29 Schwäbische Hüttenwerke Automotive GmbH Positive displacement pump with suction groove
DE102010038430B4 (en) * 2010-07-26 2012-12-06 Schwäbische Hüttenwerke Automotive GmbH Positive displacement pump with suction groove

Also Published As

Publication number Publication date
US7137798B2 (en) 2006-11-21
DE502004000102D1 (en) 2006-03-02
AT307293T (en) 2005-11-15
EP1462654B1 (en) 2005-10-19
US20040191103A1 (en) 2004-09-30
PL1462654T3 (en) 2005-12-30
ES2247580T3 (en) 2006-03-01
ATA4932003A (en) 2005-04-15
JP2004301125A (en) 2004-10-28
EP1462654A1 (en) 2004-09-29

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